Electric clutch actuator

ABSTRACT

An electric actuator for use in engaging and disengaging the clutch of a manual transmission motor vehicle. The actuator comprises an electric motor which is sized to be positioned within the housing of the clutch. The motor includes an annular armature assembly which is positioned concentrically around the clutch shaft and which drives a nut member which in turn drives a screw member to move the release bearing linearly to engage and disengage the clutch. In one embodiment, the nut and screw comprise an acme thread arrangement and in another embodiment the nut and screw are of the ball type. In one embodiment the screw advances linearly in response to rotation of the armature assembly and in another embodiment the housing and armature assembly advance linearly in response to rotation of the armature assembly while the screw remains fixed. In each of the embodiments, the motor housing, the armature assembly, the nut member, and the screw are respectively positioned concentrically within each other and concentrically about the clutch shaft to provide a compact package which slips over the clutch shaft and which is readily secured to the housing structure of the clutch and associated gear box. Relative axial movement is allowed between the release bearing and the actuator member carrying the bearing and position sensing means sense the relative positions of the release bearing and the member carrying the bearing to facilitate precise control of engagement and disengagement of the clutch.

RELATED APPLICATION

This application is a division of U.S. patent application Ser. No.119,970 filed on Nov. 13, 1987 and now U.S. Pat. No. 4,865,173.

BACKGROUND OF THE INVENTION

This invention relates to clutch assemblies for motor vehicles and moreparticularly to an electric actuator for such a clutch assembly.

Internal combustion engines require some manner of device to bridge thegap between fly wheel and gear box input speeds when the vehicle beginsto move. Such devices, with the ability to slip in a controlled manner,have taken many forms including disk clutches and torque converters. Thetorque converter allows two-pedal driving and provides smooth operation.However, it exhibits constant slip even at high speed, with associatedfuel economy disadvantages and necessitates the use of a hydrauliccircuit with consequent power losses. The manual disk clutch, bycontrast, is rugged and expensive and does not slip during normaloperation but requires attention and effort on the driver's part. In anattempt to eliminate some of the driver effort associated with a manualclutch, various actuator devices have been proposed which operate inresponse to a driver shift signal to engage and disengage the clutch,thereby relieving the driver of the clutching and declutching effort.However, the prior art clutch actuators have either not effectivelycarried out the clutching and declutching operations, have beenprohibitively expensive, or have required unacceptable levels ofmaintenance with associated warranty problems.

SUMMARY OF THE INVENTION

This invention is directed to a clutch actuator which is effective inoperation, inexpensive, and reliable over sustained periods of usage.

The invention actuator is intended for use with a motor vehicle of thetype including a disk clutch, a gear box, a clutch shaft extendingbetween the clutch and the gear box, clutch release members arrayedabout the clutch shaft and operative to engage and disengage the clutch,and a housing structure in surrounding relation to the clutch, clutchshaft, and gear box. According to the invention, the actuator includesan annular electric motor positioned in concentric surrounding relationto the clutch shaft, with the clutch shaft passing freely andconcentrically through the motor, and drive means operative in responseto energization of the motor to engage and disengage the clutch. Thisarrangement provides a compact and efficient actuator package forreadily and effectively engaging and disengaging the clutch.

According to a further feature of the invention, the actuator furtherincludes an annular clutch release bearing adapted to be positionedconcentrically around the clutch shaft between the motor and the clutchrelease members and including a non-rotating race and a rotating raceadapted to engage and rotate with the clutch release members, and thedrive means is operative in response to energization of the motor tomove the clutch release bearing axially and thereby move the clutchrelease members in a manner to engage and disengage the clutch. Thisarrangement allows the annular electric motor of the invention to beutilized in conjunction with the traditional annular clutch releasebearing to effectively engage and disengage the clutch.

According to a further feature of the invention, the motor includes anannular motor housing member sized to be mounted within the housingstructure in concentric relation to the clutch shaft and an annulararmature member positioned concentrically within the motor housingmember in concentric relation to the clutch shaft; the drive meansinclude nut means defined on the internal periphery of the annulararmature member, an annular screw member positioned concentricallywithin the armature member in threaded engagement with the nut means,and means precluding rotation of the annular screw member; and thenon-rotating bearing race of the release bearing is mounted on one ofthe actuator members. This arrangement allows the motor to be energizedto produce relative axial movement as between the various members of theactuator to thereby move the clutch release bearing axially in a senseto engage or disengage the clutch. In one disclosed embodiment of theinvention, the actuator member mounting the non-rotating bearing race isthe annular screw member and in another disclosed embodiment theactuator member mounting the non-rotating bearing race is the annularhousing member of the motor.

According to a further feature of the invention, the motor housingincludes an annular hub portion positioned concentrically within thescrew member in concentric relation to the clutch shaft and the rotationprecluding means is defined at the annular interface of the housing hubportion and the screw member. This arrangement provides a ready andeffective means of precluding rotation of the screw member and furtherprovides a firm, large area annular support surface for the screwmember.

According to a further aspect of the invention, means are provided toallow limited axial movement of the release bearing relative to theactuator member carrying the release bearing and load sensing means areprovided between the actuator member and the release bearing for sensingthe load imposed on the release bearing during release of the clutch.

According to a further feature of this aspect of the invention, the loadsensing means comprises position sensing means for sensing the relativepositions of the release bearing and the actuator member carrying therelease bearing.

According to a further feature of this aspect of the invention,resilient means are arranged between the release bearing and theactuator member carrying the release bearing to allow resilient relativemovement between the release bearing and the release member.

According to a further feature of this aspect of the invention, duringclutch release movement of the actuator member carrying the releasebearing, the actuator member moves relative to the release bearing onlyfor a limited distance whereupon continued movement of the actuatormember transmits movement to the release bearing to release the clutch.

According to a further feature of this aspect of the invention, theactuator member carrying the release bearing moves relative to therelease bearing until the release bearing abuts a surface of the membercarrying the release bearing.

According to a further feature of this aspect of the invention, theposition sensing means includes a switch which senses the relativepositions of the release bearing and the actuator member carrying therelease bearing. The switch has a switch member cooperable with one ofthe release bearing and actuator member which in one relative positionof the release bearing and actuator member occupies a first position andin a second relative position occupies a second position.

According to a further feature of this aspect of the invention, theposition sensing means comprises a first position sensing means and theactuator further includes a second position sensing means for sensingthe position of the release member during engagement and disengagementof the clutch.

According to a further feature of this aspect of the invention, controlmeans are interconnected between the first position sensing means andthe second position sensing means and the control means are operative inresponse to a signal from the first position sensing means to cause themotor to produce a predetermined amount of movement of the actuatormember carrying the release bearing to engage or disengage the clutch assensed by the second position sensing means. With this arrangement, theinitial axial movement of the selected actuator member insures that adesired amount of preload is applied to the release bearing, whereafterthe motor may be further energized to an extent to move the releasebearing axially by an amount predetermined to achieve the disengagementof the clutch.

The invention also embodies a clutch control system embodying theinvention electric clutch actuator. In one disclosed system, theelectric actuator is energized by an appropriate signal generated bydepression of the clutch pedal of the vehicle and in another disclosedsystem the clutch pedal is eliminated and the signal energizing theelectric actuator is generated by movement of the gear shift lever ofthe vehicle.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional somewhat schematic view showing theinvention electric actuator embodied in a motor vehicle clutch and gearbox assembly;

FIG. 2 is a cross-sectional view taken on line 2--2 of FIG. 1;

FIGS. 3 and 4 and detailed views taken respectively within the circles 3and 4 of FIG. 1;

FIG. 5 is a diagrammatic view of a clutch control system employing anelectric actuator according to the invention;

FIG. 6 is a view of a further clutch control system employing anelectric actuator according to the invention;

FIG. 7 is a cross-sectional view of a modified form of electric actuatoraccording to the invention;

FIGS. 8 and 9 are detailed views of a ball screw assembly employed inthe actuator of FIG. 7;

FIG. 10 is a cross-sectional view of a further modified form of electricactuator according to the invention; and

FIG. 11 is a detailed view of a motor control circuit usable in any ofthe disclosed actuator embodiments.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

The clutch and gear box assembly seen in FIG. 1 includes a clutch 10, agear box 12, and an actuator 14.

Clutch 10 is of known form and includes a clutch housing 16, a pressureplate 18, a clutch disk 20 drivingly connected to a central internallysplined hub 22, a clutch shaft 24 having a splined portion 24a at itsforward end for sliding and driving coaction with hub 22, a diaphragmspring 26 defining a plurality of circumferentially spaced clutchrelease fingers 26a, and a clutch cover 28 defining pivot posts 28apivotally mounting the clutch release finger portions 26a. It will beunderstood that cover 28 is secured to the fly wheel 30 of the vehicleand that pivotal movement of clutch release fingers 26a moves pressureplate 18 forwardly and rearwardly to selectively clamp and releaseclutch disk 20 from clamping engagement between the pressure plate andfriction material 30a carried by the rearward annular face of the flywheel so as to engage and disengage the clutch and so as to selectivelytransmit power through hub 22 and through clutch shaft 24 to gear box12.

Gear box 12 is shown in diagrammatic form and may comprise any manualgear box in which the vehicle operator may choose between a series ofgear ratios by selective movement of a gear select lever (not shown).Gear box 12 includes a housing 32 which coacts with clutch housing 16 toform a clutch and gear box housing structure. Housing 16 and 32 willnormally comprise separate housings but may, in certain applications, beformed as a single unitary housing. Housing 32 includes a forwardannular housing wall 32a passing the rearward end of clutch shaft 24.

Actuator 14 includes a motor 34, drive means 36, a release bearing 38,preload sensing means 40, and position sensing means 42.

Motor 34 includes a housing 44, permanent magnets 45, an armatureassembly 46, and brushes 48.

Housing 44 includes an annular housing member 50, an annular front endcap 52, and an annular rear end cap 54. Rear end cap 54 includes anouter annular flange portion 54a, an annular radially extending rear endwall portion 54b, and a central hollow quill or hub portion 54cextending forwardly from rear end wall portion 54b and defining anannular through passage sized to loosely pass clutch shaft 24. Housingmembers 50, 52 and 54 are clampingly held together by a plurality of tiebolts 56.

Permanent magnets 45 are of arcuate configuration and are positioned inknown manner on the circumferential interior of annular housing member50 with their adjacent ends circumferentially spaced to pass throughbolts 56.

Armature assembly 46 includes an annular armature member 58, a pluralityof laminations 60 mounted in known manner on annular armature member 58and defining axial passages 60a therebetween, windings 62 passing inknown manner through passages 60a, and a commutator 64 secured toarmature 58 rearwardly of laminations 60 and windings 62.

Brushes 48 extend between housing end cap 54 and commutator 64. Armatureassembly 46 is rotatably mounted in motor housing 44 by a front ballbearing 66 and a rear ball bearing 68, and armature assembly 46 iscaused to rotate within housing 44 in known manner upon energization ofthe armature assembly through brushes 48.

Drive means 36 includes nut means 70 defined on the inner periphery ofannular armature member 58 and an annular screw 72 including externalthreads 72a threadably coacting with nut means 70. Annular screw 72 issized to fit slidably over central housing quill 54c and is precludedfrom rotation relative to quill 54c by a key 54d carried by the quilland slidably received in a keyway 72b on the internal periphery of theannular screw. Annular screw 72 further includes a front annular hubportion 72c and a radial flange portion 72d. The coacting threads on nutmeans 70 and screw 72 may, for example, comprise acme threads.

Release bearing 38 is positioned around screw hub portion 72c proximatethe front annular face of screw flange portion 72d and includes arearward annular housing member 74, a non-rotating raceway 76 secured tothe forward annular face of housing 74, a plurality of ball bearings 78,a front annular housing member or adaptor member 80, a rotating raceway82 secured to adaptor member 80, a cage 84, and suitable seals 86 and88. A plurality of circumferentially spaced clips 90 are secured toscrew flange portion 72d. Clips 90 position the bearing in concentricrelation to screw hub portion 72c and delimit axial movement of thebearing relative to the screw hub portion. A plurality ofcircumferentially spaced prong portions 74a extend radially inwardlyfrom rearward housing member 74 for sliding engagement in grooves 72eprovided at circumferentially spaced locations on screw hub portion 72cto preclude rotation of housing 74 and associated raceway 76 relative tothe motor housing. A wave washer 91 is positioned in an annular groove72e in the forward annular face of screw flange portion 72d and urgesbearing housing member 74, and thereby bearing 38, forwardly relative toscrew hub portion 72c.

Preload sensing means 40 comprises a miniature snap action switch 92mounted on the forward annular face of screw flange portion 72d radiallyoutwardly of the forwardly extending portion 74b of non-rotating housingmember 74. Switch 92 includes a plurality of terminals 94 and a switchlever 96. Lever 96 engages housing portion 74b and is pivotable aboutits rearward end 96a to selectively control a push button 98 which inturn selectively controls terminals 94 to provide an open position forthe switch with the lever 96 in its raised position, as seen in FIG. 3,and a closed position for the switch with the lever in a loweredposition, as seen in FIG. 1. Switch 92 may, for example, comprise aswitch available from McGill Manufacturing Co. of Valparaiso, Ind., asPart No. 4906-2110 Series.

Position sensing means 42 includes an annular member 100 carried on therearward end of armature member 58, a plurality of magnet segments 100apositioned at circumferential locations about annular member 100, and aproximity switch 102, such for example as a Hall Effect switch,positioned radially outwardly of annular member 100 and mounted onhousing end cap 54.

Motor 34 is sized to be mounted within clutch housing 16 in concentricsurrounding relation to clutch shaft 24 with the clutch shaft 24 passingcentrally and freely through housing quill portion 54c for coaction withgear box 12. Motor 34 is rigidly positioned within the clutch housing bypositioning housing flange portion 54a on an annular seat 32b defined bygear box housing forward wall 32a with the flange housing 54a suitablyclamped between clutch housing 16 and the gear box housing so as tomount the actuator rigidly within the clutch housing. When mountedwithin the clutch housing, the adaptor member 80 of release bearing 38is urged into contact with the spring fingers 26a of the diaphragmspring of the clutch assembly. When motor 34 is energized throughbrushes 48, armature assembly 58 rotates, causing screw 72 to advance orretract linearly with respect to the armature assembly so as to move therelease bearing 38 forwardly or rearwardly relative to release fingers26a and respectively disengage and engage the clutch. With the clutch inits engaged position, wave washer 91 acts to urge release bearing 38forwardly with respect to screw 72, as seen in FIG. 3, so as to maintaincontact with spring fingers 26a and maintain lever 96 of switch 92 in anopen position. During the initial forward movement of screw 72 uponenergization of motor 34 in a sense to disengage the clutch, releasebearing 38 moves rearwardly relative to screw 72 with the relativemovement being allowed and resisted by wave washer 91. After apredetermined amount of such rearward movement of the bearing relativeto screw 72, lever 96, as seen in FIG. 1, moves clear of the forwardlyextending portion 74b of bearing housing member 74 to allow the lever tomove to its downwardly pivoted position in which switch 92 is closed togenerate a control signal indicating that the bearing has been preloadedto a predetermined desired extent. The preload signal would preferably,but not necessarily, be generated at such time as the radial portion 74bof housing 74 moves into bottoming engagement with the forward annularface of screw flange portion 72d, as seen in FIG. 4.

The signal thus generated by switch 92 is suitably relayed to proximityswitch 102 which proceeds to count a predetermined number of revolutionsof the armature assembly as measured by the passage of the magneticsegments 100a. After a predetermined number of revolutions of thearmature assembly has been counted, indicative of sufficient forwardlinear movement of the bearing 38 such as is required to disengage theclutch, a signal is transmitted to the motor to deenergize the motor soas to terminate forward linear movement of the screw and of the releasebearing. When it is desired to reengage the clutch, a suitable signal issent to the motor 34 to energize the motor in a sense to move screw 72linearly rearwardly. As the screw moves linearly rearwardly, the clutchis gradually engaged and the spring fingers 26a gradually pivot back totheir home or retracted position. As the fingers 26a are moving towardtheir home or retracted position, they maintain bearing 38 in a positionrelative to screw 72 wherein wave washer 91 is flattened and the rearhousing member 74 of the bearing is bottomed against screw flangeportion 76d. At such time as the spring fingers 26a arrive at their homeor retracted position, the fingers and the bearing cease movingrearwardly but the screw 72 continues to move rearwardly so thatrelative movement occurs between bearing 38 and screw 72. During thisrelative movement, wave washer 91 moves to its illustrated position ofFIG. 3 in which the bearing housing member 74 has moved away from screwflange 72d. As the bearing arrives at the position seen in FIG. 3relative to the screw, switch lever 96 is actuated upwardly to move pushbutton 98 upwardly to in turn open switch 92 and terminate theenergization of the motor so that the screw, bearing, and spring fingersare halted in their position as seen in FIG. 3.

Actuator 14 is seen in FIG. 5 embodied in a clutch and gear box controlsystem. The control system of FIG. 5, in addition to actuator 14,includes an electronic control module 104; a clutch pedal positionsensor 106 connected to control module 104 by a lead 108; leads 110 and112 connecting control module 104 to electric motor 34; a lead 114connecting module 104 to position sensor 42; and a lead 116 connectingmodule 104 to preload sensing means 40.

In the system of FIG. 5, with the clutch in its engaged position, aslight downward pivotal movement of clutch pedal 118 actuates switch 106in a sense to transmit a signal to control module 104 that the vehicleoperator desires to disengage the clutch. Control module 104 functionsin known manner to generate a signal through wires 110, 112 to energizemotor 34 in a sense to advance screw 72 of motor 34 forwardly in aclutch disengage direction. The screw 72 of the motor moves forwardlyuntil switch 92 of preload sensing means 40 generates a control signalindicating that bearing housing 74 has bottomed against screw flange 72dwhereafter control module 104 transmits a signal to position sensingmeans 42 to begin counting the revolutions of the armature assembly.After a predetermined number of revolutions have been counted,corresponding to the amount of linear movement required to achievedisengagement of the clutch, control module 104 functions to deenergizemotor 34 to hold the clutch in its disengaged position until a furtheroperator signal is received. The further operator signal, which may forexample comprise release of the clutch pedal by the vehicle operator toactuate switch 106 in the opposite sense to which it was initiallyactuated, is transmitted by control module 104 which functions toenergize motor 34 in a sense to retract screw 72. After the screw hasretracted to the point where spring fingers 26a have returned to theirretracted or home position and the screw has thereafter moved thefurther distance, as indicated in FIG. 3, necessary to move the bearinghousing 74 away from screw flange 72d, lever 96 of switch 92 is actuatedin a sense to transmit a signal to control module 104 to deenergize themotor.

In the clutch and gear box control system of FIG. 6, the clutch pedal iseliminated and the actuator 14 is controlled by movement by the gearshift lever 120 of the vehicle. In addition to actuator 14 and gearshift lever 120, the control system of FIG. 6 includes an electroniccontrol module 122; a throttle position sensor 124 connected to module122 by a lead 126; a lead 128 connecting gear shift lever 120 to controlmodule 122; an engine speed sensor 130 connected to module 122 by a lead132; a lead 134 connecting the ignition key 136 of the vehicle to module122; a lead 138 connecting preload sensing means 140 to module 122;leads 140 and 142 connecting motor 34 to module 122; a lead 144connecting position sensing means 42 to module 122; a lead 146connecting a gear box input speed sensor 148 to module 122; and a lead150 connecting a road speed sensor 152 to module 122.

In the system of FIG. 6, the signal to actuator 14 to energize anddeenergize the clutch is controlled by shift lever 120 and,specifically, the signal to disengage the clutch is generated bypressure on the lever 120, such as occurs during the shifting of lever120 from one shift position to another, and disengagement of the clutchis instigated by release of operator pressure on lever 120. Module 122receives an engage or disengage signal from shift lever 120 and, if thesignals received from throttle position sensor 124, engine speed sensor130, gear box input speed sensor 148, and road speed sensor 152 arecompatible with the requested engage or disengage action, transmits theappropriate control signal through leads 140, 142 to motor 34 to movescrew 72 linearly in a sense to engage or disengage the clutch withpreload sensing means 40 and position sensing means 42 functioning inthe manner described with respect to the detailed description ofactuator 14 and with respect to the control system of FIG. 5.

A modified form of actuator is disclosed in FIG. 7. The actuator seen inFIG. 7 is generally similar to the actuator of FIG. 1 with theexceptions that the nut means 70 of FIG. 1 is constituted by a separateball nut 154 positioned concentrically and fixedly within armature 58;the central hollow quill 54c of the housing is eliminated; screw 72 isconstituted by a ball screw 156; a radial flange portion 156a of theball screw extends outwardly beyond the outer perimeter of bearing 38and radially beyond switch 92; ball screw 156 further includes anaxially extending annular cover portion 156b positioned radiallyoutwardly of housing annular member 50 to provide a dust and contaminateshield for the motor 34; and the position sensing means 42 comprises apotentiometer 158 positioned on the outer periphery of ball screw coverportion 156b and coacting with a fixed rod 160 secured to housing endcap 54 by a bracket 162 to provide an instantaneous indication of theaxial position of screw 156 relative to motor housing 44. Ball nut 154and ball screw 156 may be of any known type but preferably are of theinternal ball return type wherein, after each turn, and as best seen inFIGS. 8 and 9, the balls 163 are fed back to the previous turn by afloating liner situated inside the nut. The actuator of FIG. 7 operatesin the control system of FIG. 5 or the control system of FIG. 6 in thesame manner previously described with respect to the actuator of FIG. 1.

The actuator of FIG. 10 is generally similar to the actuator of FIG. 1with the exception that the nut means 70 of FIG. 1 is replaced by a ballnut 164; the screw 72 of FIG. 1 is replaced by a ball screw 166 having amain body threaded portion 166a for threaded coaction with ball nut 164and a radial flange portion 166b adapted to be fixedly secured to gearbox end wall 132a; the motor housing 44 includes a rear end cap 168defining a plurality of axial bores 168a and a front end cap 170; thefront end cap 170 carries switch 92 and release bearing 38; and aplurality of guide pins 170 are secured to gear box front wall 32a andextend forwardly therefrom through ball screw flange portion 166b forsliding receipt in bores 168a of rear housing end cap 168. In theoperation of the actuator of FIG. 10, energization of the motor 34 andconsequent rotation of armature assembly 46 results in axial movement ofmotor housing 44 along guide pins 172 with a consequent linear movementof release bearing 38 to engage and disengage the clutch in the mannerpreviously described with respect to the FIG. 1 and the FIG. 7embodiments of the actuator. The position sensor 42 in the FIG. 7embodiment comprises a potentiometer 174 secured to housing member 50and coacting with a fixed rod 176 fixed to ball screw flange portion166b to provide an instantaneous indication of the axial position of thehousing relative to the fixed portions of the actuator. The actuator ofFIG. 10 functions in the control system of FIG. 5 or the control systemof FIG. 6 in a manner similar to the operation described with respect tothe actuator of FIG. 1.

Whereas, in each of the disclosed actuator embodiments, the back EMF ofthe motor 34 in combination with the lead of the nut and screw of thedrive means will normally be sufficient to preclude back driving of themotor by the clutch assembly with the clutch in its disengaged position,it may be necessary in some applications to augment the back EMF of themotor and the resistance provided by the lead of the nut and screwassembly by the use of dynamic braking of the motor. Specifically, asseen in FIG. 11, the motor 34 may be made a part of an H-bridge in whichswitches A and B are provided in the two positive leads 178 and 180 andfurther switches C and D are provided in negative leads 182 and 184 ofthe H-bridge. With this H-bridge arrangement, the motor may be driven ina forward sense by the closing of switches A and B; may be driven in abackward or rearward sense by the closing of switches B and C; and maybe dynamically braked by the closing either of switches A and B or ofswitches C and D. The switching of the switches A, B, C and D may becontrolled in a known manner by the control module 104 of the controlsystem of FIG. 5 or the control module 122 of the control system of FIG.6. In either system, the appropriate module will function upon thearrival of the clutch at its fully disengaged or fully engaged positionto close either switches A and B or switches C and D to therebydynamically brake the motor. The dynamic breaking action not onlyserves, with the clutch in its disengaged position, to augment theresistance to back driving provided by the lead of the nut and screw andthe back EMF of the motor, but also functions to provide a more rapidand more precise stoppage of the motor at such time as the clutch hasarrived at either its fully disengaged or fully engaged position.

The invention electric clutch actuator will be seen to provide acompact, inexpensive and reliable means of readily engaging anddisengaging the clutch of the associated motor vehicle so as to retainthe ruggedness, lack of slip, and low cost of a manual transmissionarrangement while substantially eliminating the driver effort requiredto achieve the necessary clutch engagement and disengagement duringchanging of the gear ratios of the associated gear box.

Whereas preferred embodiments of the invention have been illustrated anddescribed in detail, it will be apparent that various changes may bemade in the disclosed embodiments without departing from the scope orspirit of the invention. For example, whereas the invention clutchactuator has been illustrated and described in association with apush-type clutch assembly wherein the rotating race of the releasebearing pushingly engages the clutch release members, the inventionclutch actuator may also be employed in association with a pull-typeclutch wherein the rotating race of the release bearing pullinglyengages the clutch release members.

We claim:
 1. A drive transmission for a vehicle including a clutchthrough which drive is to be transmitted to a gear box and a clutchrelease mechanism for engaging or disengaging the clutch, the clutchrelease mechanism including an axially movable release member and ananti-friction release bearing comprising relatively rotatable racesarranged between the release member and clutch in a manner to allowlimited relative axial movement between the release bearing and therelease member, and load sensing means, including means positionedbetween the release member and the release bearing, operative to sensethe load imposed on the release bearing during release of the clutch. 2.A drive transmission according to claim 1 wherein said load sensingmeans comprises position sensing means for sensing the relativepositions of the release bearing and release member.
 3. A drivetransmission according to claim 2 wherein during clutch release movementof said release member the release member moves relative to said releasebearing only for a limited distance whereupon continued movement of therelease member transmits movement of the release bearing to release theclutch.
 4. A drive transmission according to claim 3 wherein the releasemember moves relative to said release bearing until the release bearingabuts a surface of said release member.
 5. A drive transmissionaccording to claim 2 wherein the position sensing means includes aswitch which senses the relative positions.
 6. A drive transmissionaccording to claim 5 wherein the switch has a switch member cooperablewith one of the release bearing and release member whereby in onerelative position the switch member occupies a first position and in asecond relative position the switch occupies a second position.
 7. Adrive transmission according to claim 2 wherein the position sensingmeans is mounted on the release member.
 8. An actuator for use with amotor vehicle of the type including a disk clutch, a gear box, a clutchshaft extending between the clutch and the gear box, and clutch releaseelements arrayed about the clutch shaft and operative to engage anddisengage the clutch, said actuator comprising:a clutch release membermovable axially in response to operator actuation of the clutch; anaxially movable anti-friction release bearing comprising relativelyrotatable races arranged between the release member and the clutchrelease elements; means allowing relative axial movement between theclutch release member and the release bearing; means operative to sensethe relative axial position of said release bearing and said releasemember; and means operative to generate a control signal in response toa sensed predetermined relative axial position of said release bearingand said release member.
 9. An actuator according to claim 8 wherein,during clutch release movement of said release member, the releasemember moves relative to the release bearing only for a limiteddistance, whereupon continued movement of the release member transmitsmovement to the release bearing to release the clutch.
 10. An actuatoraccording to claim 9 wherein the release member moves relative to therelease bearing until the release bearing abuts a surface of saidrelease member.
 11. An actuator according to claim 8 wherein the loadsensing means includes a switch which senses the relative positions ofthe release bearing and the release member.
 12. An actuator according toclaim 11 wherein the switch has a switch member cooperable with one ofthe release bearing and release member whereby in one relative positionthe switch member occupies a first position and in a second relativeposition the switch member occupies a second position.
 13. An actuatoraccording to claim 8 wherein the load sensing means is mounted betweenthe release member and the release bearing.
 14. A drive transmission fora vehicle including a clutch through which drive is to be transmitted toa gear box and a clutch release mechanism for engaging or disengagingthe clutch, the clutch release mechanism including a movable releasemember and a release bearing arranged between the release member andclutch in a manner to allow limited relative axial movement between therelease bearing and the release member, and load sensing meanspositioned between the release member and the release bearing forsensing the load imposed on the release bearing during release of theclutch, resilient means being arranged between the release bearing andthe release member to permit resilient relative movement between therelease bearing and the release member.
 15. A drive transmissionaccording to claim 14 wherein the resilient means is a wave washer. 16.A drive transmission for a vehicle including a clutch through whichdrive is to be transmitted to a gear box and a clutch release mechanismfor engaging or disengaging the clutch, the clutch release mechanismincluding a movable release member and a release bearing arrangedbetween the release member and clutch in a manner to allow limitedrelative axial movement between the release bearing and the releasemember, a first position sensing means positioned between the releasemember and the release bearing for sensing the load imposed on therelease bearing during release of the clutch, and a second positionsensing means for sensing the position of the release member duringengagement and disengagement of the clutch.
 17. A drive transmissionaccording to claim 16 wherein a motor is provided for moving the releasemember and wherein control means are interconnected between the firstposition sensing means and the second position sensing means, thecontrol means being operative in response to a signal from the firstposition sensing means to cause the motor to produce a predeterminedamount of movement of the release member to engage or disengage theclutch as sensed by said second position sensing means.
 18. An actuatorfor use with a motor vehicle of the type including a disk clutch, a gearbox, a clutch shaft extending between the clutch and the gear box, andclutch release elements arrayed about the clutch shaft and operative toengage and disengage the clutch, said actuator comprising:a clutchrelease member movable in response to operator actuation of the clutch;a release bearing arranged between the release member and the clutchrelease elements; means allowing relative axial movement between theclutch release member and the release bearing; and load sensing means,including resilient means arranged between the release bearing and therelease member to permit resilient relative movement between the releasebearing and the release member, for sensing the load imposed on therelease bearing during release of the clutch.
 19. An actuator accordingto claim 18 wherein the resilient means comprises a wave washer.
 20. Anactuator according to claim 18 wherein a motor is provided to move therelease member and wherein control means are interconnected between thefirst position sensing and the second position sensing means, thecontrol means being operative in response to a signal from the firstposition sensing means to cause the motor to produce a predeterminedamount of movement of the release member to engage or disengage theclutch as sensed by said second position sensing means.
 21. An actuatorfor use with a motor vehicle of the type including a disk clutch, a gearbox, a clutch shaft extending between the clutch and the gear box, andclutch release elements arrayed about the clutch shaft and operative toengage and disengage the clutch, said actuator comprising:a clutchrelease member movable in response to operator actuation of the clutch;a release bearing arranged between the release member and the clutchrelease elements; means allowing relative axial movement between theclutch release member and the release bearing; a first position sensingmeans for sensing the load imposed on the release bearing during releaseof the clutch; and second position sensing means for sensing theposition of the release member during engagement and disengagement ofthe clutch.